EP1775444A1 - Engine de travaux à piston - Google Patents
Engine de travaux à piston Download PDFInfo
- Publication number
- EP1775444A1 EP1775444A1 EP06021047A EP06021047A EP1775444A1 EP 1775444 A1 EP1775444 A1 EP 1775444A1 EP 06021047 A EP06021047 A EP 06021047A EP 06021047 A EP06021047 A EP 06021047A EP 1775444 A1 EP1775444 A1 EP 1775444A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- housing
- working machine
- crankshaft
- crankshafts
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/06—Engines with means for equalising torque
- F02B75/065—Engines with means for equalising torque with double connecting rods or crankshafts
Definitions
- the invention relates to a piston working machine with at least one dry-running piston-cylinder unit.
- Such piston working machines are known, for example, as cross-head piston working machines in which the piston is divided into two, wherein a first, upper piston portion with the wall of the cylinder determines the cylinder volume and wherein a second, lower piston portion spaced from the first piston portion via a piston rod in the lower region of the cylinder is guided.
- a lubricant supply for the second piston region is provided in this lower region of the cylinder.
- the lower and the upper part of the cylinder are sealed against each other, wherein the piston rod between the two cylinder sections penetrates this seal.
- the first, upper portion of the piston runs without additional lubricant in the cylinder.
- the advantage of such a dry-running cylinder is in that no lubricant is introduced into the compression space of the cylinder, so that when the piston-cylinder unit is used as a compressor, no lubricant is introduced into the gas to be compressed. Even if the piston-cylinder unit is designed as a pump, no lubricant is transported into the fluid to be pumped. But even if the dry-running piston working machine is designed as an internal combustion engine, no lubricant is introduced into the combustion chamber, so that the exhaust gas performance of the internal combustion engine is improved.
- Object of the present invention is therefore to provide a piston working machine with at least one dry-running piston-cylinder unit, which is compact and ensures reliable operation of the piston in the cylinder even at high operating performance.
- the embodiment according to the invention as a double crankshaft piston working machine has the advantage that, due to the crankshafts rotating synchronously in opposite directions, the cylinder connected to the crankshafts via in each case one connecting rod is not subjected to tilting forces and is therefore reliably guided in the cylinder. As a result, the additional guidance required in the cross-head piston working machine can be eliminated by means of a second piston section in the lower region of the cylinder.
- crankshafts of the piston working machine are stored in a lubricant-supplied separate housing and can exit from this sealingly with its end portion, the entire crank mechanism of the cylinder can be provided outside of the lubricant-supplied housing, so that there is no risk of the entry of lubricant in the compression space of the piston-cylinder unit.
- the synchronization gears are also arranged within the lubricant supplied with the second housing.
- the second housing is integrally formed with the first housing.
- the respective connecting rod is mounted on the associated crank pin and the associated reciprocating means sealed against the escape of lubricant bearing, so that the required for the conrod bearing lubricant does not penetrate into the interior of the dry first housing and from there on the piston over in can get the compression space.
- the two crankshafts are mounted within the second housing in at least one common bearing block, wherein the bearing block consists of a material having a first coefficient of thermal expansion, wherein the synchronization gears are made of a material having a second coefficient of thermal expansion and wherein the dimensions of the bearing block and the synchronization gears in the radial direction and the first and second coefficients of thermal expansion are coordinated so that the thermal expansion of the bearing block between the two axes of rotation is substantially equal to the thermal expansion of the synchronization gears.
- the common storage of the two crankshafts in at least one common bearing block initially allows forces, which act in the radial direction between the two crankshafts, do not have to be routed through the housing, but are absorbed directly in the bearing block.
- the housing can therefore be designed for low weight.
- the particular choice of materials of the bearing block and the intermeshing synchronization gears wherein the dimensions of the bearing block and the synchronization gears in the radial direction and the first coefficient of thermal expansion of the material of the bearing block and the second coefficient of thermal expansion of the material of the synchronization gears are coordinated so that the thermal expansion of the bearing block between the two axes of rotation is substantially equal to the thermal expansion of the synchronization gears, also ensures that the backlash between the two intermeshing synchronization gears remains constant and does not change in temperature fluctuations that occur especially in high-performance engines. As a result, the wear load of the tooth flanks and the noise are noticeably reduced.
- crankshafts are made of a material having a third coefficient of thermal expansion and that the dimensions of the bearing block, the crankshafts and the gears in the radial direction and the first, second and third coefficients of thermal expansion are coordinated so that the Thermal expansion of the bearing block and the crankshaft sections mounted therein is substantially equal to the thermal expansion of the timing gears and crankshaft sections on which the timing gears are mounted.
- the thermal properties of the crankshafts are taken into account in the compensation of the thermal influences on the backlash.
- bearing block and the synchronization gears each consist of material with the same coefficient of thermal expansion, wherein advantageously also the crankshafts made of the material with this coefficient of thermal expansion.
- bearing block and the synchronization gears are made of the same material and, if advantageously, the crankshafts also consist of the same material.
- At least two storage chairs are provided for supporting the crankshafts.
- a further advantageous embodiment of the invention is characterized in that also the other end of the respective crankshaft is led out of the second housing and that each of the crankshafts is also provided at the other end with a crank pin, each having an associated connecting rod with a cylinder of a second piston-cylinder unit is connected.
- piston working machine is either compressors, pumps or internal combustion engines.
- the piston working machine can also be designed as a multi-stage compressor or as a multi-stage pump.
- piston-cylinder units are designed as a dry-running pump or dry-running compressor, while the other piston-cylinder unit is designed as an internal combustion engine for driving the pump or the compressor.
- piston-cylinder unit can be designed either as a dry-running piston-cylinder unit or as a conventionally lubricated piston-cylinder unit.
- a reciprocating piston 3 is arranged to be movable back and forth.
- a cylinder space or compression space 20 is enclosed by the wall of the cylinder 2 and the upper end face of the piston crown 30 of the cylinder 2.
- an inlet valve 22 and an outlet valve 24 are provided, which connect the compression chamber 20 with a - not shown - inlet channel or - not shown - outlet channel.
- the piston 3 is at its circumference in the region of its piston crown 30 with two axially spaced-apart piston rings 31, 32 and a remote from the piston crown 30 lower piston region guide ring 33rd Mistake.
- the guide ring 33 and / or the piston rings 31, 32 are made of a material with self-lubricating properties, such as PTFE (polytetrafluoroethylene) or graphite.
- the piston 3 is provided with two connecting pins 34, 35 which are offset laterally relative to one another with respect to the cylinder axis A.
- each connecting rod 6, 7 is rotatably mounted on an associated crank pin 40, 50 by means of a respective sealed against the escape of lubricant roller bearing, each of which forms a crankshaft-side connecting rod bearing 41, 51.
- the first crank pin 40 is provided on a crankshaft 42 connected to a first crankshaft 4 and the second crank pin 50 is provided on a crankshaft 52 connected to a second crankshaft 5.
- the first crankshaft 4 and the second crankshaft 5 run parallel to one another and rotate synchronously in opposite directions.
- the axes of rotation X, X 'of the two crankshafts 4, 5 run parallel to a common cylinder center plane Z and are offset laterally symmetrically with respect to this cylinder center plane Z.
- Fig. 2 is a longitudinal section through the piston working machine in the direction of arrows II-II in Fig. 1 is shown.
- the cylinder 2 is bounded at the top by a cylinder head and is connected at the bottom in a conventional manner to a first housing 1 of the piston working machine.
- a first housing 1 of the piston working machine Within the first Housing 1 of the crank disks 42, 52 and the connecting rods 6, 7 existing crank mechanism for the piston 3 is provided.
- a second housing 8 Integral with the first housing 1, a second housing 8 is formed, which is delimited and sealed by a partition wall 12 relative to the first housing 1.
- the second housing 8 encloses a second housing space 80 and has an oil pan 82 in its lower area.
- the oil pan 82 and a lower portion of the housing interior 80 are filled with a lubricating oil.
- crankshafts 4, 5 are mounted such that each of the crankshafts 4, 5' is mounted in each of the two bearing blocks 9, 9 '.
- the respective crankshaft 4, 5 is formed cylindrical within the second housing 8 and in each case by a arranged in the partition wall 12 radial seal, of which in Fig. 2, only the crankshaft 4 associated radial seal 43 is shown, from the interior 80 of the second housing eighth led out into the interior 10 of the first housing 1.
- the other end of at least one of the two crankshafts is led out on the end wall 84 of the housing 8 facing away from the partition 12 through a radial seal 44 arranged in this end wall 84.
- This lead-out end of the at least one crankshaft when the piston working machine is a compressor or a pump, serves as the drive shaft for the piston working machine and, when the piston working machine is an internal combustion engine, as the output shaft.
- crankshafts 4, 5 is non-rotatable within the housing 8 with one on the cylindrical crankshaft section 45 mounted synchronization gear 46, 56, wherein the synchronization gears 46, 56 meshing with each other and dive with its lower portion in the lubricant reservoir 81 in the lower region of the interior 80 of the housing 8.
- crankshaft bearings to be lubricated and the timing gears to be lubricated 46, 56 within the second housing 8
- the bearings required here the connecting rods are formed by encapsulated bearings that are sealed against leakage of lubricant, so that in the cylinder 2 no lubricant can occur.
- the double crankshaft arrangement in conjunction with the piston 3 articulated via the two connecting rods 6, 7 ensures that no tilting forces act on the piston 3, so that it is always guided with its piston center axis A 'in the direction of the cylinder axis A.
- the preferably made of self-lubricating material guide ring 33 assumes a centering of the piston 3 in the cylinder 2 and the piston rings 31, 32 provide a seal of the compression chamber 20 against the connected to the interior of the housing 1 lower part of the interior of the cylinder. 2
- the device according to the invention may also assume other than the above-described embodiments.
- the device can in particular features comprising a combination of the respective individual features of the claims.
- the portion of the cylindrical crankshaft portion 45 that emerges from the second housing 8 and forms a drive shaft or an output shaft for the piston working machine 45 may be provided with a pulley or with a gear for transmitting power, for example, when the piston working machine is a compressor or a pump Gear on the drive shaft, which meshes with other gears in a radial drive, is preferred because this leads to a particularly compact design.
- further units such as, for example, an oil pump, can be connected to drive them.
- the piston working machine according to the invention if designed as a compressor, can also contain a plurality of compressor stages and thus form a two-stage or multi-stage compressor.
- crankshaft is then not designed as a front crankshaft, but has conventional crank sections, which provided in the first housing 1 and are stored accordingly.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Reciprocating Pumps (AREA)
- Compressor (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PL06021047T PL1775444T3 (pl) | 2005-10-11 | 2006-10-06 | Tłokowa maszyna robocza |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005048681A DE102005048681B4 (de) | 2005-10-11 | 2005-10-11 | Kolbenarbeitsmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1775444A1 true EP1775444A1 (fr) | 2007-04-18 |
EP1775444B1 EP1775444B1 (fr) | 2008-06-18 |
Family
ID=37547568
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06021047A Not-in-force EP1775444B1 (fr) | 2005-10-11 | 2006-10-06 | Engine de travaux à piston |
Country Status (6)
Country | Link |
---|---|
US (1) | US7240647B2 (fr) |
EP (1) | EP1775444B1 (fr) |
AT (1) | ATE398725T1 (fr) |
DE (2) | DE102005048681B4 (fr) |
ES (1) | ES2308639T3 (fr) |
PL (1) | PL1775444T3 (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102388210A (zh) * | 2009-04-15 | 2012-03-21 | 亨德里克斯·约翰·斯维尼克 | 对往复式活塞发动机的扭矩输出的增加 |
Families Citing this family (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2456305A (en) * | 2008-01-09 | 2009-07-15 | Jeremy Fox | Short stroke internal combustion engine with two connecting rods and two crankshafts per cylinder |
DE102008011959A1 (de) | 2008-03-01 | 2009-09-03 | Wabco Gmbh | Kolbenmaschine mit wenigstens zwei Wellen |
US8474435B2 (en) * | 2008-09-04 | 2013-07-02 | Achates Power, Inc. | Opposed piston, compression ignition engine with single-side mounted crankshafts and crossheads |
US8485161B2 (en) * | 2008-09-04 | 2013-07-16 | Achates Power, Inc. | Opposed piston, compression ignition engine with single-side mounted crankshafts and crossheads |
DE102009005447A1 (de) | 2009-01-21 | 2010-07-22 | Wabco Gmbh | Kolbenmaschine |
US9797341B2 (en) * | 2009-07-01 | 2017-10-24 | New Power Concepts Llc | Linear cross-head bearing for stirling engine |
JP5588564B2 (ja) * | 2010-08-05 | 2014-09-10 | ダルケ,アーサー,イー. | デュアルクランク軸内燃機関 |
US8360028B2 (en) * | 2010-09-04 | 2013-01-29 | Neander Motors | Piston with two pivot bearings and twin crankshaft piston engine |
US9856866B2 (en) | 2011-01-28 | 2018-01-02 | Wabtec Holding Corp. | Oil-free air compressor for rail vehicles |
DE102011015720A1 (de) * | 2011-03-31 | 2012-10-04 | Neander Motors Ag | Hubkolbenmaschine, vorzugsweise als Kompressor, Pumpe, Kompressionsmaschine oder dgl. wirkend |
DE102011110037A1 (de) | 2011-08-12 | 2013-02-14 | Neander Motors Ag | Hubkolbenmaschine mit einem Kurbeltrieb |
DE102011112653A1 (de) * | 2011-09-07 | 2013-03-07 | Neander Motors Ag | Hubkolbenmaschine, vorzugsweise der Bauart Brennkraftmaschine |
DE102015013631A1 (de) * | 2015-10-21 | 2017-04-27 | Neander Motors Ag | Schwenklager für zwei Pleuel |
CN112135965B (zh) * | 2019-02-14 | 2022-05-31 | 株式会社石川能源研究 | 动力单元 |
US11674434B2 (en) | 2020-07-02 | 2023-06-13 | Impact Consulting And Engineering Llc | Multiple cylinder engine |
US11635020B2 (en) | 2020-07-02 | 2023-04-25 | Fna Group, Inc. | Multiple cylinder engine |
US11506119B2 (en) * | 2020-07-02 | 2022-11-22 | Impact Consulting And Engineering Llc | Multiple cylinder engine |
US11603793B2 (en) | 2020-07-02 | 2023-03-14 | Fna Group, Inc. | Multiple cylinder engine |
DE102021115568A1 (de) | 2021-06-16 | 2022-12-22 | Neander Motors Aktiengesellschaft | Verbrennungsmotor mit Kolben |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB450804A (en) * | 1935-12-02 | 1936-07-24 | Ragnar Berggren | Improvements in or relating to internal combustion engines having pistons situated opposite each other |
US2229788A (en) * | 1939-03-14 | 1941-01-28 | Appleton Thomas Jay | Dual crankshaft engine |
US4614169A (en) * | 1983-06-09 | 1986-09-30 | Figliuzzi Vincent D | Ultra high compression engine |
US4936262A (en) * | 1985-12-05 | 1990-06-26 | Paul Marius A | Regenerative thermal engine |
DE4013754A1 (de) * | 1990-04-14 | 1991-10-17 | Heinz Evers | Kolbenmaschine |
US5179921A (en) * | 1992-01-30 | 1993-01-19 | Vincent Figliuzzi | Integrated engine and compressor device |
US5339779A (en) * | 1990-10-26 | 1994-08-23 | Zettner Michael L | Piston connection for a reciprocating piston engine |
US6152098A (en) * | 1998-01-14 | 2000-11-28 | Andreas Stihl Ag & Co. | Internal combustion engine for a portable handheld work apparatus |
DE10019959A1 (de) * | 2000-04-20 | 2001-10-25 | Gerhard Klaiber | Brennkraftmaschine |
US6447268B1 (en) * | 2000-11-28 | 2002-09-10 | John Abramopaulos | Positive displacement engine with integrated positive displacement rotary fluid compressor |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4690113A (en) * | 1986-04-30 | 1987-09-01 | Olivier Deland | Internal combustion engine |
DE10348345B4 (de) * | 2003-10-17 | 2005-09-01 | Neander-Motorfahrzeuge Gmbh | Hubkolben-Brennkraftmaschine |
-
2005
- 2005-10-11 DE DE102005048681A patent/DE102005048681B4/de not_active Expired - Fee Related
- 2005-11-10 US US11/272,457 patent/US7240647B2/en not_active Expired - Fee Related
-
2006
- 2006-10-06 EP EP06021047A patent/EP1775444B1/fr not_active Not-in-force
- 2006-10-06 DE DE502006000943T patent/DE502006000943D1/de active Active
- 2006-10-06 ES ES06021047T patent/ES2308639T3/es active Active
- 2006-10-06 AT AT06021047T patent/ATE398725T1/de not_active IP Right Cessation
- 2006-10-06 PL PL06021047T patent/PL1775444T3/pl unknown
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB450804A (en) * | 1935-12-02 | 1936-07-24 | Ragnar Berggren | Improvements in or relating to internal combustion engines having pistons situated opposite each other |
US2229788A (en) * | 1939-03-14 | 1941-01-28 | Appleton Thomas Jay | Dual crankshaft engine |
US4614169A (en) * | 1983-06-09 | 1986-09-30 | Figliuzzi Vincent D | Ultra high compression engine |
US4936262A (en) * | 1985-12-05 | 1990-06-26 | Paul Marius A | Regenerative thermal engine |
DE4013754A1 (de) * | 1990-04-14 | 1991-10-17 | Heinz Evers | Kolbenmaschine |
US5339779A (en) * | 1990-10-26 | 1994-08-23 | Zettner Michael L | Piston connection for a reciprocating piston engine |
US5179921A (en) * | 1992-01-30 | 1993-01-19 | Vincent Figliuzzi | Integrated engine and compressor device |
US6152098A (en) * | 1998-01-14 | 2000-11-28 | Andreas Stihl Ag & Co. | Internal combustion engine for a portable handheld work apparatus |
DE10019959A1 (de) * | 2000-04-20 | 2001-10-25 | Gerhard Klaiber | Brennkraftmaschine |
US6447268B1 (en) * | 2000-11-28 | 2002-09-10 | John Abramopaulos | Positive displacement engine with integrated positive displacement rotary fluid compressor |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102388210A (zh) * | 2009-04-15 | 2012-03-21 | 亨德里克斯·约翰·斯维尼克 | 对往复式活塞发动机的扭矩输出的增加 |
Also Published As
Publication number | Publication date |
---|---|
US7240647B2 (en) | 2007-07-10 |
EP1775444B1 (fr) | 2008-06-18 |
DE502006000943D1 (de) | 2008-07-31 |
PL1775444T3 (pl) | 2009-01-30 |
ATE398725T1 (de) | 2008-07-15 |
DE102005048681B4 (de) | 2007-08-09 |
DE102005048681A1 (de) | 2007-05-10 |
US20070079788A1 (en) | 2007-04-12 |
ES2308639T3 (es) | 2008-12-01 |
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